US20020152887A1 - Cooling arrangement for an inclined-axis variable displacement unit - Google Patents
Cooling arrangement for an inclined-axis variable displacement unit Download PDFInfo
- Publication number
- US20020152887A1 US20020152887A1 US09/948,985 US94898501A US2002152887A1 US 20020152887 A1 US20020152887 A1 US 20020152887A1 US 94898501 A US94898501 A US 94898501A US 2002152887 A1 US2002152887 A1 US 2002152887A1
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- United States
- Prior art keywords
- variable displacement
- displacement unit
- unit according
- axis variable
- pivoting body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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- 238000006073 displacement reaction Methods 0.000 title claims abstract description 26
- 238000001816 cooling Methods 0.000 title claims description 35
- 239000002826 coolant Substances 0.000 claims description 28
- 230000002706 hydrostatic effect Effects 0.000 claims description 3
- 238000011010 flushing procedure Methods 0.000 claims 1
- 230000001360 synchronised effect Effects 0.000 claims 1
- 238000010276 construction Methods 0.000 description 5
- 238000007789 sealing Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/328—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the axis of the cylinder barrel relative to the swash plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2064—Housings
Definitions
- the invention relates to an inclined-axis variable displacement unit or an axial piston machine of inclined-axis construction.
- a cooling arrangement is particularly important in axial piston machines of inclined-axis construction, in particular when relatively high levels of power are to be transferred. Insufficient cooling adversely affects the service life since the signs of wear increase at high operating temperatures. Moreover, with improved cooling, higher rotational speeds and larger maximum external diameters of the bearings are possible, these factors being of considerable importance as far as the service life of axial piston machines is concerned.
- Axial piston machines of inclined-axis construction in which the bearings are cooled by oil which is located in the housing of the machine are already known.
- the oil here is fed on by a pump effect which is produced by the rotation of the roller mounting.
- a disadvantage of this solution is that it is essentially only the oil which is located in the immediate vicinity of the mounting and is already at elevated temperature which is circulated.
- this oil has already cooled other internals of the machine beforehand, with the result that the viscosity has already been reduced, an elevated oil temperature resulting in a reduction in the viscosity.
- Patent DE-A-196 49 195 discloses a cooling arrangement for an axial piston machine in which the operating medium is guided, from a low-pressure branch of the main circuit of the motor, through a cooling channel which extends in the central part of the cylinder block and along the axis of rotation of the shaft.
- a disadvantage of this solution is that the oil is likewise heated en route to the bearings in the central part of the motor.
- this arrangement of a cooling channel restricts the throughflow cross section to a considerable extent, with the result that the quantity of oil flowing through for cooling is vastly reduced.
- Patent DE-A-198 29 060 discloses a means for cooling an axial piston machine in which the oil used as coolant is introduced directly at the mounting. The coolant then passes through the mounting into the housing interior, in which the cylinder drum is located.
- a branch line runs from the coolant stream along the axis of rotation of the shaft and then through the central part of the cylinder block.
- this line rather than being provided for cooling purposes, is only provided for lubricating the synchronizing articulation.
- the principal object of the present invention is to provide an inclined-axis variable displacement unit or an axial piston machine of inclined-axis construction in which the service life is increased.
- An inclined-axis variable displacement unit has an output shaft ( 1 ), mounted in a housing ( 4 ), and a cylinder block ( 10 ), the cylinder block ( 10 ) being connected to the output shaft ( 1 ) via a synchronizing articulation ( 13 ), and via working pistons ( 11 ) which can be displaced in the cylinder block ( 10 ), and the cylinder block ( 10 ) being mounted in a pivoting body ( 5 ) which can be pivoted in relation to the axis of the output shaft, it being the case that the pivoting body ( 5 ) is in the form of an open vessel, and the cylinder block ( 10 ) is arranged in the opening of the pivoting body.
- FIG. 1 shows a cross section of the cylinder block and of the inclined-axis variable adjustment unit according to the invention in the plane defined by the axis of the output shaft, said cross section illustrating the course taken by the central cooling channel and the coolant guide space:
- FIG. 2 shows a section through the selector valve and the flushing-pressure-limiting valve
- FIG. 3 shows a cross section of the pivoting body perpendicular to the drawing plane according to FIG. 1;
- FIG. 4 shows a section along line A-A according to FIG. 3;
- FIG. 5 shows a section along line B-B according to FIG. 3.
- FIG. 1 illustrates a housing 4 of the unit, within which a pivoting body 5 is mounted.
- a cylinder block 10 Located within the pivoting body 5 , in turn, is a cylinder block 10 , which is mounted axially in the pivoting body 5 .
- the cylinder block 10 is connected to the shaft 1 via synchronizing articulation 13 .
- the shaft 1 is mounted in the housing 4 with the aid of rolling-contact bearings 2 and 3 , although it is also possible to provide slide bearings.
- the shaft 1 is connected to a group of working pistons 11 , which are mounted displaceably in cylinder openings 12 of the cylinder block 10 .
- the cylinder block 10 is mounted pivotably in the housing 4 with the aid of an axial pivoting body 5 .
- the mounting of the pivoting body 5 and the supply of the oil into the cylinder block are described in more detail hereinbelow.
- the operating fluid passes from a low-pressure line of the inclined-axis variable displacement unit through the selector valve 30 and the flushing-pressure-limiting valve 31 , via the pressure channel 32 , into an inlet cooling space 34 .
- the function of the selector valve 30 and of the flushing- pressure-limiting valve 31 is explained in more detail hereinbelow.
- a central cooling channel 35 connects the inlet cooling space 34 to the discharge space 36 .
- Said central cooling channel 35 runs first of all through the shaft 1 , then through the synchronizing articulation 13 and the cylinder block 10 , and finally opens out into the discharge space 36 by way of an outlet channel 39 .
- a coolant guide space 37 likewise connects the inlet cooling space 34 to the discharge space 36 .
- the coolant guide space 37 is bounded by the rolling-contact bearing 2 , the housing 4 , the pivoting body 5 and the cylinder block 10 .
- the oil passes from the inlet cooling space 34 , through the rolling-contact bearings 2 and 3 , into the coolant guide space 37 .
- the pivoting body 5 is in the form of a vessel, of which the edge 8 separates the coolant guide space 37 from the discharge space 36 of the housing 4 .
- Part of the interior of the housing 4 comprises walls which are made up of arc segments 7 , these arc segments 7 being located in the immediate vicinity of the edges 8 of the pivoting body 5 .
- Located in the vicinity of the base of the pivoting body 5 is an outlet channel 38 , which connects the coolant guide space 37 to the discharge space 36 .
- the oil thus passes over two routes from the inlet cooling space 34 into the discharge space 36 .
- the throughflow divides, in relation to the hydraulic flow resistances of the central cooling channel 35 and of the coolant guide space 37 , into two oil-mass streams.
- a possible pump effect of the bearings is also to be taken into account here, however.
- the two oil-mass streams combine in the discharge space 36 , in which the same pressure level prevails.
- the oil flowing through removes the heat generated from the inclined-axis variable displacement unit.
- the oil leaves the discharge space 36 through the opening 40 and flows on from there preferably to a cooler.
- Supplying oil to the machine in a single hydraulic circuit is the preferred embodiment. However, it is also possible, within the scope of the invention, to provide two hydraulic circuits, of which one is provided in the machine for the conversion into a rotary movement and the other is provided for cooling the machine.
- FIG. 2 shows a cross section through the selector valve 30 and the flushing-pressure-limiting valve 31 .
- the slide within the selector valve 30 is controlled by pressure lines abutting 35 laterally, that is to say at the top and bottom in FIG. 2.
- the pivoting body 5 is subdivided into two symmetrical cylinder segments 51 and 52 . These cylinder segments 51 and 52 form an imaginary cylindrical plane 53 which intersects the space in which the working pistons 11 and the cylinder block 10 are mounted.
- non-stationary transfer channels 56 a and 56 b are arranged in the respective cylinder segments, the top ends of the channels opening out into throughflow chambers 54 a ′ and 54 b ′.
- the operating fluid is supplied and discharged via these channels 44 a and 44 b, depending on the direction of rotation of the shaft.
- the plane of the hydrostatic slide mounting for the pivoting body 5 which coincides with the imaginary cylinder plane 53 , is thus located in the region of said throughflow chambers 54 a, 54 b, 54 a ′ and 54 b′.
- FIG. 4 represents a sectional illustration along line A-A according to FIG. 3, i.e. along the cylinder plane 53 .
- FIG. 4 it is possible to see the corresponding openings of the non-stationary transfer channels 56 a and 56 b, the openings of the stationary transfer channels 44 a and 44 b and the throughflow chambers 54 a and 54 b.
- These throughflow chambers 54 a and 54 b extend, transversely to the openings of the respective transfer channels, over more or less the entire length of the cylinder segments 51 and 52 .
- the cylinder segments 51 and 52 are provided with corresponding compensation chambers 55 a and 55 b.
- the compensation chambers 55 a and 55 b like the throughflow chambers 54 a and 54 b, are enclosed by corresponding sealing zones 541 a and 541 b.
- the compensation chamber 55 a is connected to the circle-segment channel 57 b via a connecting channel 58 a
- the compensation chamber 55 b is connected to the circle-segment channel 57 a via a corresponding connecting channel 58 b.
- the pressure signal is then fed to said compensation chambers 55 a and 55 b, via the connecting channels 58 a and 58 b, from the non-stationary transfer channels 56 b and 56 a on the opposite side of the pivoting body 5 .
- the diameter of the cylinder segments 51 and 52 in the configuration according to the present invention is considerably smaller than the respective configurations from the prior art, the length of that stretch which each point of the imaginary cylindrical plane 53 has to cover during adjustment of the pivoting body 5 is also shorter. It is thus always possible to provide a sufficient throughflow width for the throughflow chambers 54 a and 54 b. At the same time, it is possible to mount the pivoting body 5 in the stationary part of the housing 4 in the vicinity of the separating plane 45 of the housing 4 . In this way, the vibrations of the housing 4 which occur on account of the cyclic loading of the pivoting body 5 , can be reduced to a considerable extent. As can be seen in FIG. 2, the end side 21 of the rolling-contact bearing 2 is thus located in the separating plane 45 of the housing 4 .
- FIG. 5 shows a section along B-B according to FIG. 3, i.e. a section through the left-hand cylinder segment 52 and the corresponding portion of the housing 4 .
- the latter has the stationary transfer channel 44 b, which then opens out into the throughflow chamber 54 b.
- the cylinder segment 52 is mounted for hydrostatic sliding action in the hollow 42 , while the opposite end is connected to the stationary part of the housing 4 by axially displaceable pins 14 .
- the circle-segment channel 57 b is arranged in the base 6 of the pivoting body 5 .
- the non-stationary transfer channel 56 b which connects the segment channel 57 b to the throughflow chamber 54 b, is configured by two parallel channels.
- the vessel-like form of the pivoting body allows the coolant stream to be guided past the cylinder block in a controlled manner. It is possible here for the pivoting body, which may be configured in one or more parts, to engage either fully or just partially around the cylinder block and to have openings on its base, and on its side walls.
- Dividing up the interior of the housing into a coolant guide space and into a discharge space prevents the low-temperature coolant from being mixed prematurely with the already heated coolant, as is the case, for example in the configuration described in Patent DE-A-198 29 060.
- the temperature distribution of the coolant from the inlet cooling space, via the coolant guide space, to the discharge space is thus favorably influenced and largely predetermined.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
An inclined-axis variable displacement unit has an output shaft (1), mounted in a housing (4), and a cylinder block (10), the cylinder block (10) being connected to the output shaft (1) via a synchronizing articulation (13), and via working pistons (11) which can be displaced in the cylinder block (10), and the cylinder block (10) being mounted in a pivoting body (5) which can be pivoted in relation to the axis of the output shaft, it being the case that the pivoting body (5) is in the form of an open vessel, and the cylinder block (10) is arranged in the opening of the pivoting body.
Description
- The invention relates to an inclined-axis variable displacement unit or an axial piston machine of inclined-axis construction.
- The generally known operating principle of such machines is based on an oil-volume stream being converted into a rotary movement.
- A cooling arrangement is particularly important in axial piston machines of inclined-axis construction, in particular when relatively high levels of power are to be transferred. Insufficient cooling adversely affects the service life since the signs of wear increase at high operating temperatures. Moreover, with improved cooling, higher rotational speeds and larger maximum external diameters of the bearings are possible, these factors being of considerable importance as far as the service life of axial piston machines is concerned.
- Axial piston machines of inclined-axis construction in which the bearings are cooled by oil which is located in the housing of the machine are already known. The oil here is fed on by a pump effect which is produced by the rotation of the roller mounting. A disadvantage of this solution, however, is that it is essentially only the oil which is located in the immediate vicinity of the mounting and is already at elevated temperature which is circulated. Moreover, this oil has already cooled other internals of the machine beforehand, with the result that the viscosity has already been reduced, an elevated oil temperature resulting in a reduction in the viscosity.
- Patent DE-A-196 49 195 discloses a cooling arrangement for an axial piston machine in which the operating medium is guided, from a low-pressure branch of the main circuit of the motor, through a cooling channel which extends in the central part of the cylinder block and along the axis of rotation of the shaft. A disadvantage of this solution, however, is that the oil is likewise heated en route to the bearings in the central part of the motor. Moreover, this arrangement of a cooling channel restricts the throughflow cross section to a considerable extent, with the result that the quantity of oil flowing through for cooling is vastly reduced.
- Finally, Patent DE-A-198 29 060 discloses a means for cooling an axial piston machine in which the oil used as coolant is introduced directly at the mounting. The coolant then passes through the mounting into the housing interior, in which the cylinder drum is located. In this case, a branch line runs from the coolant stream along the axis of rotation of the shaft and then through the central part of the cylinder block. However, this line, rather than being provided for cooling purposes, is only provided for lubricating the synchronizing articulation.
- The principal object of the present invention is to provide an inclined-axis variable displacement unit or an axial piston machine of inclined-axis construction in which the service life is increased.
- This object is achieved by an inclined-axis variable displacement unit or an axial piston machine of inclined-axis construction.
- An inclined-axis variable displacement unit has an output shaft (1), mounted in a housing (4), and a cylinder block (10), the cylinder block (10) being connected to the output shaft (1) via a synchronizing articulation (13), and via working pistons (11) which can be displaced in the cylinder block (10), and the cylinder block (10) being mounted in a pivoting body (5) which can be pivoted in relation to the axis of the output shaft, it being the case that the pivoting body (5) is in the form of an open vessel, and the cylinder block (10) is arranged in the opening of the pivoting body.
- FIG. 1 shows a cross section of the cylinder block and of the inclined-axis variable adjustment unit according to the invention in the plane defined by the axis of the output shaft, said cross section illustrating the course taken by the central cooling channel and the coolant guide space:
- FIG. 2 shows a section through the selector valve and the flushing-pressure-limiting valve;
- FIG. 3 shows a cross section of the pivoting body perpendicular to the drawing plane according to FIG. 1;
- FIG. 4 shows a section along line A-A according to FIG. 3; and
- FIG. 5 shows a section along line B-B according to FIG. 3.
- FIG. 1 illustrates a housing4 of the unit, within which a
pivoting body 5 is mounted. Located within thepivoting body 5, in turn, is acylinder block 10, which is mounted axially in the pivotingbody 5. Thecylinder block 10 is connected to the shaft 1 via synchronizing articulation 13. The shaft 1 is mounted in the housing 4 with the aid of rolling-contact bearings 2 and 3, although it is also possible to provide slide bearings. The shaft 1 is connected to a group of workingpistons 11, which are mounted displaceably incylinder openings 12 of thecylinder block 10. - The
cylinder block 10 is mounted pivotably in the housing 4 with the aid of anaxial pivoting body 5. The mounting of thepivoting body 5 and the supply of the oil into the cylinder block are described in more detail hereinbelow. - The operating fluid passes from a low-pressure line of the inclined-axis variable displacement unit through the selector valve30 and the flushing-pressure-limiting
valve 31, via thepressure channel 32, into aninlet cooling space 34. The function of the selector valve 30 and of the flushing- pressure-limitingvalve 31 is explained in more detail hereinbelow. - A
central cooling channel 35 connects theinlet cooling space 34 to thedischarge space 36. Saidcentral cooling channel 35 runs first of all through the shaft 1, then through the synchronizing articulation 13 and thecylinder block 10, and finally opens out into thedischarge space 36 by way of anoutlet channel 39. - A
coolant guide space 37 likewise connects theinlet cooling space 34 to thedischarge space 36. Thecoolant guide space 37 is bounded by the rolling-contact bearing 2, the housing 4, thepivoting body 5 and thecylinder block 10. The oil passes from theinlet cooling space 34, through the rolling-contact bearings 2 and 3, into thecoolant guide space 37. For this connection, however, it is also possible—preferably if slide bearings are used—to provide a separate channel either in the housing 4 or in the shaft 1. - The
pivoting body 5 is in the form of a vessel, of which the edge 8 separates thecoolant guide space 37 from thedischarge space 36 of the housing 4. Part of the interior of the housing 4 comprises walls which are made up of arc segments 7, these arc segments 7 being located in the immediate vicinity of the edges 8 of thepivoting body 5. Located in the vicinity of the base of thepivoting body 5 is anoutlet channel 38, which connects thecoolant guide space 37 to thedischarge space 36. - The better the pivoting
body 5 is sealed in relation to the housing 4, the more effective is the cooling of the rolling-contact bearings 2 and 3 and of thecylinder block 10, since, with perfect sealing, the entire oil-mass stream which passes into the coolant guide space is guided directly past thecylinder block 10 and only then passes, through theoutlet channel 38, into thedischarge space 36. Moreover, the flow from theinlet cooling space 34 to thedischarge space 36 is controlled, the oil used as coolant still being at a minimal temperature in the region of the rolling-contact bearings. Mixing with coolant that has already been heated does not take place. It should be emphasized, however, that the invention functions even when no sealing is provided between thepivoting body 5 and the housing 4. In this case, however, the gap between these components should be configured to be as small as possible, e.g. by the edge 8 being positioned as closely as possible to the arc segments 7 of the housing 4. - By virtue of the above described provision of a
central cooling channel 35, on the one hand, and of acoolant guide space 37, on the other hand, the oil thus passes over two routes from theinlet cooling space 34 into thedischarge space 36. In theinlet cooling space 34, the throughflow divides, in relation to the hydraulic flow resistances of thecentral cooling channel 35 and of thecoolant guide space 37, into two oil-mass streams. A possible pump effect of the bearings is also to be taken into account here, however. The two oil-mass streams combine in thedischarge space 36, in which the same pressure level prevails. - En route out of the inlet cooling space into the discharge space, the oil flowing through removes the heat generated from the inclined-axis variable displacement unit. The oil leaves the
discharge space 36 through theopening 40 and flows on from there preferably to a cooler. - Supplying oil to the machine in a single hydraulic circuit is the preferred embodiment. However, it is also possible, within the scope of the invention, to provide two hydraulic circuits, of which one is provided in the machine for the conversion into a rotary movement and the other is provided for cooling the machine.
- FIG. 2 shows a cross section through the selector valve30 and the flushing-pressure-limiting
valve 31. The slide within the selector valve 30 is controlled by pressure lines abutting 35 laterally, that is to say at the top and bottom in FIG. 2. - These pressure lines are connected to the inflow and outflow line for the cylinder drum. With a changeover in the pressure conditions in these lines, the desired direction of rotation of the axial piston machine also changes. With such a changeover, the slide is displaced within the selector valve30, with the result that the
pressure channel 33 is always connected to the respective low-pressure line of the axial piston machine. - As can be seen in FIG. 3, the pivoting
body 5 is subdivided into twosymmetrical cylinder segments cylinder segments cylindrical plane 53 which intersects the space in which the workingpistons 11 and thecylinder block 10 are mounted. - It can be seen that
non-stationary transfer channels throughflow chambers 54 a′ and 54 b′. Thesethroughflow chambers 54 a′ and 54 b′ overlap withthroughflow chambers stationary transfer channels channels - The plane of the hydrostatic slide mounting for the pivoting
body 5, which coincides with theimaginary cylinder plane 53, is thus located in the region of saidthroughflow chambers - FIG. 4 represents a sectional illustration along line A-A according to FIG. 3, i.e. along the
cylinder plane 53. In this view, it is possible to see the corresponding openings of thenon-stationary transfer channels stationary transfer channels throughflow chambers throughflow chambers cylinder segments body 5, thecylinder segments corresponding compensation chambers compensation chambers throughflow chambers zones compensation chamber 55 a is connected to the circle-segment channel 57 b via a connectingchannel 58 a, while thecompensation chamber 55 b is connected to the circle-segment channel 57 a via a corresponding connectingchannel 58 b. - The pressure signal is then fed to said
compensation chambers channels non-stationary transfer channels body 5. - Since the diameter of the
cylinder segments cylindrical plane 53 has to cover during adjustment of the pivotingbody 5 is also shorter. It is thus always possible to provide a sufficient throughflow width for thethroughflow chambers body 5 in the stationary part of the housing 4 in the vicinity of the separating plane 45 of the housing 4. In this way, the vibrations of the housing 4 which occur on account of the cyclic loading of the pivotingbody 5, can be reduced to a considerable extent. As can be seen in FIG. 2, the end side 21 of the rolling-contact bearing 2 is thus located in the separating plane 45 of the housing 4. - FIG. 5 shows a section along B-B according to FIG. 3, i.e. a section through the left-
hand cylinder segment 52 and the corresponding portion of the housing 4. The latter has thestationary transfer channel 44 b, which then opens out into thethroughflow chamber 54 b. Thecylinder segment 52 is mounted for hydrostatic sliding action in the hollow 42, while the opposite end is connected to the stationary part of the housing 4 by axially displaceable pins 14. The circle-segment channel 57 b is arranged in the base 6 of the pivotingbody 5. In the exemplary embodiment shown here, thenon-stationary transfer channel 56 b, which connects thesegment channel 57 b to thethroughflow chamber 54 b, is configured by two parallel channels. - The vessel-like form of the pivoting body allows the coolant stream to be guided past the cylinder block in a controlled manner. It is possible here for the pivoting body, which may be configured in one or more parts, to engage either fully or just partially around the cylinder block and to have openings on its base, and on its side walls.
- Dividing up the interior of the housing into a coolant guide space and into a discharge space prevents the low-temperature coolant from being mixed prematurely with the already heated coolant, as is the case, for example in the configuration described in Patent DE-A-198 29 060. The temperature distribution of the coolant from the inlet cooling space, via the coolant guide space, to the discharge space is thus favorably influenced and largely predetermined.
- It is therefore seen that this invention will achieve its principal objective.
List of designations 1 Output shaft 2 First rolling-contact bearing 3 Second rolling-contact bearing 4 Housing 5 Pivoting body 6 Base of the pivoting body 7 Arc-segment-like inner surfaces 8 Edge 10 Cylinder block 11 Working piston 12 Cylinder openings in the cylinder block 13 Synchronizing articulation 14 Pin 21 End side of the first rolling-contact bearing 30 Selector valve 31 Flushing-pressure-limiting valve 32 Channel 33 Pressure channel 34 Inlet cooling space 35 Central cooling channel 36 Discharge space 37 Coolant guide space 38 First outlet channel 39 Second outlet channel 40 Opening 41, 42 Hollows 44a, 44b Stationary transfer channels 45 Separating plane of the housing 51, 52 Cylinder segments 53 Imaginary cylinder plane 54a, 54b Throughflow chambers in the housing 54a′, 54b′ Throughflow chambers in the pivoting body 55a, 55b Compensation chambers 56a, 56b Non-stationary transfer channels 57a, 57b Circle- segment channels 58a, 58b Connecting channels 541a, 541b Sealing zones
Claims (18)
1. An inclined-axis variable displacement unit comprising an output shaft (1), mounted in a housing (4), and a cylinder block (10), the cylinder block (10) being connected to the output shaft (1) via a synchronizing articulation (13), and via working pistons (11) which can be displaced in the cylinder block (10), and being mounted in a pivoting body (5), which can be pivoted in relation to the axis of the output shaft, characterized in that
the pivoting body (5) is in the form of an open vessel, the cylinder block (10) being arranged in the opening of the pivoting body (5).
2. The inclined-axis variable displacement unit according to claim 1 , characterized in that the pivoting body (5) divides up the interior of the housing into a coolant guide space (37) and a discharge space (36), the coolant guide space (37) being bounded on the one hand by the interior of the pivoting body (5) and, on the other hand by the mounting of the output shaft (1).
3. The inclined-axis variable displacement unit according to claim 1 , characterized in that the pivoting body (5) has one or more first outlet channels (38) which connect the coolant guide space (37) and the discharge space (36) to one another.
4. The inclined-axis variable displacement unit according to one of claim 1 , characterized in that the first outlet channel or channels (38) is/are arranged in the region of the base of the vessel-like pivoting body (5).
5. The inclined-axis variable displacement unit according to claim 1 , characterized in that part of the housing (4) has one or more inner surfaces (7) which is/are located in the immediate vicinity of the edge (8) of the opening of the vessel-like pivoting body (5).
6. The inclined-axis variable displacement unit according to claim 1 , characterized in that at least one inner surface (7), which is located in the immediate vicinity of the edge (8) of the opening of the vessel like pivoting body (5), has an arc-segment shape.
7. The inclined-axis variable displacement unit according to claim 1 , characterized in that the pivoting body (5) is mounted for hydrostatic sliding action in the housing (4).
8. The inclined-axis variable displacement unit according to claim 1 , characterized in that the pivoting body (5) is formed in one or more pieces.
9. The inclined-axis variable displacement unit according to claim 1 , characterized in that the pivoting body (5) engages fully or partially around the cylinder block (10).
10. The inclined-axis variable displacement unit according to claim 1 , characterized in that an inlet cooling space (34) is located on a side of the mounting of the output shaft (1) which is directed away from the cylinder block (10).
11. The inclined-axis variable displacement unit according to claim 1 , characterized in that the inlet cooling space (34) is connected to the coolant guide space (37).
12. The inclined-axis variable displacement unit according to claim 1 , characterized in that there is provided a central cooling channel (35) which connects the inlet cooling space (34) and the discharge space (36) to one another.
13. The inclined-axis variable displacement unit according to claim 1 , characterized in that the central cooling channel (35) runs through the synchronized articulation (13) and the cylinder block (10).
14. The inclined-axis variable displacement unit according to claim 1 , characterized in that the central cooling channel (35) runs through the output shaft (1).
15. The inclined-axis variable displacement unit according to claim 1 , characterized in that the central cooling channel (35) opens out into the discharge space (36) by way of a second outlet channel (39), which is arranged in the pivoting body (5).
16. The inclined-axis variable displacement unit according to claim 1 , characterized in that the oil used as coolant passes into the interior of the housing via a selector valve (30).
17. The inclined-axis variable displacement unit according to claim 1 , characterized in that a low-pressure branch of the main circuit of said unit is provided for the coolant circulation.
18. The inclined-axis variable displacement unit according to claim 1 , characterized in that a flushing pressure-limiting valve (31) is provided for the coolant circulation.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10044785 | 2000-09-11 | ||
DE10044785.6 | 2000-09-11 | ||
DE2000144785 DE10044785C2 (en) | 2000-09-11 | 2000-09-11 | Cooling device for an inclined axis adjustment unit |
Publications (2)
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US20020152887A1 true US20020152887A1 (en) | 2002-10-24 |
US6505541B2 US6505541B2 (en) | 2003-01-14 |
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US09/948,985 Expired - Fee Related US6505541B2 (en) | 2000-09-11 | 2001-09-07 | Cooling arrangement for an inclined-axis variable displacement unit |
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US (1) | US6505541B2 (en) |
DE (1) | DE10066008B4 (en) |
Cited By (2)
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US20060054416A1 (en) * | 2002-10-31 | 2006-03-16 | Per-Ola Vallebrant | Device for reducing energy losses in a machinery unit |
WO2011087576A2 (en) | 2009-12-22 | 2011-07-21 | Parker Hannifin Corporation | Hydraulic machine with oil dams |
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US7305915B2 (en) * | 2004-03-08 | 2007-12-11 | The United States Of America As Represented By The Administrator Of The Environmental Protection Agency | Efficient pump/motor with reduced energy loss |
CN100529389C (en) * | 2004-10-20 | 2009-08-19 | 马库斯利布赫尔国际公司 | Hydrostatic axial piston machine and use of said machine |
DE102007051369B4 (en) * | 2007-10-26 | 2010-06-10 | Sauer-Danfoss Gmbh & Co Ohg | Hydrostatic slant axis engine with a synchronizing joint for angularly adjustable drive connection of a cylinder block with a drive shaft |
DE102018215362A1 (en) * | 2018-09-11 | 2020-03-12 | Robert Bosch Gmbh | Axial piston machine |
DE102018218040A1 (en) * | 2018-10-22 | 2020-04-23 | Danfoss Power Solutions Gmbh & Co. Ohg | SYNCHRONIZATION JOINT |
CN114001005B (en) * | 2021-11-02 | 2023-06-23 | 河南科技大学 | Hydraulic plunger pump |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
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US2661701A (en) * | 1947-10-03 | 1953-12-08 | Oilgear Co | Axial type hydrodynamic machine |
US3277835A (en) * | 1964-07-07 | 1966-10-11 | Gunnar A Wahlmark | Fluid device |
US3760692A (en) * | 1970-12-16 | 1973-09-25 | H Molly | Axial piston type machine |
FR2135776A5 (en) * | 1971-04-28 | 1972-12-22 | Renault | |
FR2427486A1 (en) * | 1978-06-02 | 1979-12-28 | Centre Techn Ind Mecanique | MULTICYLINDRICAL HYDRAULIC PUMP / MOTOR WITH BARREL, VARIABLE CYLINDER |
FR2566468B1 (en) * | 1984-06-22 | 1986-10-03 | Renault | DEVICE FOR DRIVING A ROTATING PUMP OR HYDRAULIC MOTOR CYLINDER BLOCK |
DE19649195C1 (en) * | 1996-11-27 | 1998-01-08 | Brueninghaus Hydromatik Gmbh | Axial piston machine with swivelling cylinder drum |
DE19829060B4 (en) * | 1998-06-29 | 2007-01-04 | Brueninghaus Hydromatik Gmbh | Hydrostatic machine with backwater device in the lubrication channel |
-
2000
- 2000-09-11 DE DE10066008A patent/DE10066008B4/en not_active Expired - Fee Related
-
2001
- 2001-09-07 US US09/948,985 patent/US6505541B2/en not_active Expired - Fee Related
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060054416A1 (en) * | 2002-10-31 | 2006-03-16 | Per-Ola Vallebrant | Device for reducing energy losses in a machinery unit |
US7325477B2 (en) * | 2002-10-31 | 2008-02-05 | Parker-Hannifin Corporation | Device for reducing energy losses in a machinery unit |
WO2011087576A2 (en) | 2009-12-22 | 2011-07-21 | Parker Hannifin Corporation | Hydraulic machine with oil dams |
WO2011087576A3 (en) * | 2009-12-22 | 2013-01-17 | Parker Hannifin Corporation | Hydraulic machine with oil dams |
JP2013515204A (en) * | 2009-12-22 | 2013-05-02 | パーカー・ハニフィン・コーポレーション | Hydraulic device with oil dam |
CN103124850A (en) * | 2009-12-22 | 2013-05-29 | 帕克-汉尼芬公司 | Hydraulic machine with oil dams |
Also Published As
Publication number | Publication date |
---|---|
DE10066008B4 (en) | 2004-04-22 |
DE10066008A1 (en) | 2002-03-28 |
US6505541B2 (en) | 2003-01-14 |
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